EP3086075B1 - Wärmetauschervorrichtung - Google Patents

Wärmetauschervorrichtung Download PDF

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Publication number
EP3086075B1
EP3086075B1 EP16165749.9A EP16165749A EP3086075B1 EP 3086075 B1 EP3086075 B1 EP 3086075B1 EP 16165749 A EP16165749 A EP 16165749A EP 3086075 B1 EP3086075 B1 EP 3086075B1
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EP
European Patent Office
Prior art keywords
baffle
tubes
shell
bundle
coolant liquid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16165749.9A
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English (en)
French (fr)
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EP3086075A1 (de
Inventor
José Antonio GRANDE FERNÁNDEZ
Germán Troncoso
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BorgWarner Emissions Systems Spain SL
Original Assignee
BorgWarner Emissions Systems Spain SL
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Priority to EP16165749.9A priority Critical patent/EP3086075B1/de
Publication of EP3086075A1 publication Critical patent/EP3086075A1/de
Application granted granted Critical
Publication of EP3086075B1 publication Critical patent/EP3086075B1/de
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1638—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/06—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with the heat-exchange conduits forming part of, or being attached to, the tank containing the body of fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0236—Header boxes; End plates floating elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0236—Header boxes; End plates floating elements
    • F28F9/0241—Header boxes; End plates floating elements floating end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/24—Arrangements for promoting turbulent flow of heat-exchange media, e.g. by plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/32—Liquid-cooled heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1653—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0236—Header boxes; End plates floating elements
    • F28F9/0239—Header boxes; End plates floating elements floating header boxes

Definitions

  • the present invention relates to a heat exchange device of the so-called floating core type, having a special configuration which allows increasing its durability as it increases its thermal fatigue resistance.
  • This invention is characterized by a configuration having high thermal fatigue resistance due to the special configuration of the end where the floating side of the core is located since stagnation regions that are usually produced in the baffle of the floating end are eliminated by means of the combination of the shape of the shell and of a deflector. This configuration furthermore results in a low-cost exchanger.
  • the device can be applied in EGR (Exhaust Gas Recirculation) systems the use of which in internal combustion engines reduces the emission of contaminant gases, thus protecting the environment.
  • EGR exhaust Gas Recirculation
  • An exemplary such heat exchanging device is known from EP2728155 A1 .
  • heat exchangers formed by a shell housing a bundle of exchange tubes where this bundle of tubes extends between two baffles have the drawback of differential expansion occurring between the shell, directly in contact with the coolant liquid, and in the bundle of tubes, also in direct contact with the hot gas to be cooled.
  • Differential expansion between one component and another is particularly pronounced in the longitudinal direction established by the main direction along which the bundle of tubes extends.
  • the core is the bundle of heat exchange tubes where the tubes are attached at least between two end baffles.
  • One baffle is conjoint with the shell and the other baffle, i.e., the baffle corresponding to the floating end, allows relative movement with respect to the shell.
  • the baffle that allows movement is usually connected, according to the particular configuration of the exchanger, by means of an elastically deformable element establishing the fluid continuity of the hot gas conduit and it is the one which allows thermal expansion.
  • Both fixed and movable baffles are walls located transverse to the bundle of tubes. If the hot gas inlet is at the floating end, the movable baffle is the one that is subjected to higher temperature. Given that the baffle is movable, the coolant liquid flow tends to flow around the perimetral area of the baffle. This condition leads to a stagnation point or region causing the coolant liquid to remain in the hot area without discharging heat until reaching the boiling temperature. This is one of the causes generating thermal fatigue and failure of the device.
  • the present invention proposes a particular configuration of a floating core device in which the existence of stagnation regions in the baffle on the floating side is prevented, preventing thermal fatigue and therefore prolonging the service life of the device.
  • the present invention relates to a heat exchange device adapted for cooling a hot gas by means of a coolant liquid, particularly configured for preventing thermal fatigue, solving the drawbacks identified above.
  • the device comprises:
  • the heat exchanger has a floating core configuration.
  • the core is formed by a bundle of exchange tubes extending between two baffles, a first baffle which is conjoint with the shell, hence it is referred to as a fixed baffle, and a second floating or movable baffle due to the effect of differential expansion with respect to the shell.
  • the expansion compensated for by the floating core configuration is the expansion in the direction of the exchange tubes. This is the direction identified as longitudinal direction X-X'.
  • the baffles are usually arranged transverse to the longitudinal direction.
  • the exchange tubes are tubes through which the hot gas to be cooled passes, and they are externally surrounded by the coolant liquid.
  • the coolant liquid circulates through the space located between the outer surface of the tubes of the bundle of tubes and the shell.
  • the shell also extends according to longitudinal direction X-X'. It is closed at one end by the fixed baffle.
  • the shell comprises at the opposite end an extension configured by means of a segment located at the end opposite the end containing the fixed baffle and the section of which is larger.
  • the larger section of this end segment forms a chamber.
  • the final end of the shell on the side of the chamber formed by the segment having a larger section is closed by a third baffle.
  • One particular way of providing the extension is by means of two tubular bodies having different sections, i.e., a first tubular body having a smaller section, housing primarily the bundle of tubes, and a second tubular body having larger dimensions located right after the end of the first tubular body.
  • the transition between the first tubular body and the second tubular body can be configured by means of a transition body formed by a transition surface between the section of the first tubular body and the section of the second tubular body. This transition surface establishes continuity between the first body and the second body assuring leak-tightness between them. If the tubular bodies have a circular section, the transition surface can be ring-shaped or even funnel-shaped.
  • the heat exchanger can operate under co-current or counter-current flow. Therefore, accesses to the inner space of the shell intended for the coolant liquid are identified as inlet/outlet. There are at least two accesses for the entry and exit of the coolant liquid, a first access located at a point of the shell on the side of the first baffle, i.e., close to the first baffle, and the other access is located on the opposite side located in a position of the shell segment having a larger section. If one of the accesses serves as an inlet then the other one is the outlet.
  • the device provides that:
  • the second baffle or floating baffle of the bundle of tubes is therefore located between the first baffle and the third baffle in a position such that it is housed in the chamber formed by the extension of the shell.
  • Enlargement in longitudinal direction X-X' is mainly due to the longitudinal expansion of the bundle of tubes so the assembly formed by the second baffle and the manifold distributing hot gas at the inlet of the exchange tubes of the bundle of tubes will move inside this chamber.
  • the longitudinal expansion of the entire core establishes a degree of approaching the third baffle and is compensated for by the deformation capability of the elastically deformable conduit connecting the hot gas inlet of the heat exchanger and the manifold.
  • Hot gas therefore enters through an opening of the third baffle and gains access to the manifold through the elastically deformable conduit.
  • the inside of the manifold is in fluid communication with the inside of the exchange tubes such that the hot gas is distributed for passing inside the exchange tubes of the bundle of tubes.
  • the hot gas transfers its heat to the coolant liquid and reaches the opposite end of the tubes, i.e., the end located in the first baffle.
  • the cooled gas is collected, for example, by means of another outer manifold, and used for final use thereof as an EGR gas, for example.
  • the heat exchanger can operate under co-current or counter-current flow.
  • the coolant liquid enters the shell on the fixed side of the core and flows towards the second baffle.
  • the flow is guided by the shell segment that does not correspond to the extension and is therefore arranged against the exchange tubes since reducing the space between the exchange tubes and the shell reduces the presence of paths having lower resistance which favor preventing flow passage between the exchange tubes, reducing the effectiveness thereof.
  • This flow reaches the second baffle which is located, together with the manifold, in the chamber formed by the extension of the shell.
  • this assembly formed by the second floating baffle-manifold is spaced by means of a separation space with the inner wall of the shell segment having a larger section surrounding them, the flow following a longitudinal direction tends to flow around the baffle in order to pass through the perimetral space.
  • the streamlines corresponding to this flow would extend longitudinally and, upon reaching the baffle, they would get around it through any of the points in the periphery thereof. If, for example, the baffle has a rectangular configuration and four sides, there is a stagnation point with this configuration corresponding to the lines that do not lead to any of the four sides. If, for example, the baffle is circular, then the stagnation point would be the central area of the baffle since the flow lines would not have a preferred position in the periphery for getting around the second baffle.
  • the invention prevents this stagnation region by including a deflector closing the separation space between the assembly formed by the floating baffle together with the manifold and the extended segment of the shell. This deflector closes the space at least along a perimetral segment. In the counter-current example that is being described, the deflector is located downstream with respect to the second baffle.
  • this deflector is to prevent the passage of most of the flow lines therethrough allowing only the passage through a perimetral portion of said deflector. Additionally, with this deflector it has been observed that the trajectory of the streamlines located on the side of the second baffle in contact with the coolant liquid is modified because a velocity field parallel to said second baffle is created, minimizing and even eliminating stagnation points. Stagnation points are eliminated by a sweeping effect due to a flow parallel to the baffle identified with the streamlines essentially parallel to the baffle in the proximity thereof. This has the effect of increasing coolant velocity with respect to the hot baffle, i.e., the second baffle, significantly increasing the level of cooling thereof and therefore reducing thermal stresses therein.
  • the present invention relates to a heat exchange device adapted for cooling a hot gas by means of a coolant liquid.
  • a heat exchange device adapted for cooling a hot gas by means of a coolant liquid.
  • One of the uses of this exchanger is to cool part of the combustion gases produced by an internal combustion engine in order to reintroduce them in the intake forming part of an EGR system.
  • Figure 1 shows one embodiment of the invention, a heat exchanger with a floating core configuration formed by a shell (1) in which, in this embodiment, the section of the shell (1) is essentially rectangular.
  • the fixed side of the exchanger is shown on the left side of Figure 1 , fixed being understood as the core of the exchanger being conjoint with the shell, and the side where the core is floating and allows thermal expansion in longitudinal direction X-X' is shown on the right side.
  • the exchanger of the embodiment has on the fixed side a fixing flange (6) which allows screwing the exchanger, for example, to a manifold not depicted in the drawing for the sake of clarity, which manifold receives the outlet gases from said exchanger once they have been cooled.
  • the heat exchanger has a bundle of tubes (4) extending from a first baffle (2) conjoint with the shell (1) to a second floating baffle (3), i.e., not conjoint with the shell (1).
  • the first baffle has dimensions greater than the section of the shell (1) such that the flange (6) presses this first baffle (2), for example, against a second flange of the manifold that is not shown.
  • the bundle of tubes (4) has a plurality of support baffles (5) distributed along the length thereof that are either conjoint with the shell (1) and without restricting longitudinal movement of the bundle of tubes (4) passing therethrough or conjoint with the bundle of tubes (4) passing therethrough and without restricting longitudinal movement with respect to the shell (1).
  • the support baffles (5) the generation of stresses due to differential expansion of the exchange tubes (4) with respect to the shell (1) is prevented.
  • the support action of these support baffles (5) is with respect to the transverse direction, for example, preventing inertial effects due to mechanical vibrations, and it also establishes a flow with transverse components increasing heat exchange between the bundle of tubes (4) and the coolant liquid circulating inside the shell (1).
  • the exchange tubes are hybrid tubes, i.e., having an essentially planar configuration and containing therein a bent plate forming fins increasing the effective exchange surface to facilitate heat transfer from the hot gas to the coolant liquid covering the outside of the exchange tubes (4). Nevertheless, it is possible to use another tube configuration without modifying the essential features of the invention.
  • the floating end of the heat exchanger shows an extension of the shell (1).
  • the extension is achieved using two tubular bodies, a first tubular body (1) arranged against the bundle of tubes (4) where one of the ends is the side conjoint with the first baffle (2), and a second tubular body, a shell segment (7) having a larger section, making up the end segment located at the opposite end of the exchanger according to longitudinal direction X-X'.
  • first tubular body of the shell (1) and the second tubular body, the shell segment (7) having a larger section are attached by means of a transition part (13) configured by a deep-drawn and die-cut plate.
  • This transition part (13) receives the first tubular body of the shell (1) on one side and receives the shell segment (7) having a larger section on the opposite side, such that this transition part defines the extension region of the first tubular body of the shell (1).
  • the second baffle (3) is located at the floating end of the bundle of tubes (4).
  • the exchange tubes of the bundle of tubes (4) are attached to this second baffle (3) and this second baffle (3) is in turn attached to a manifold (9) which is in communication with the hot gas inlet.
  • the manifold (9) receives incoming hot gases and distributes the gas through the inlets of the exchange tubes (4) such that the hot gas is forced to enter the exchange tubes (4).
  • the second baffle (3) is configured by means of a die-cut and stamped plate surrounding the manifold (9) where the contact area between both parts (3, 9) is an attachment by means of brazing.
  • the manifold (9) is connected with the end of the exchanger on the floating side by means of an elastically deformable conduit (10).
  • the elastically deformable element (10) is a bellow-shaped metal conduit.
  • the closure of the shell at the floating end where the shell segment (7) formed by a tubular body having a larger section is located, is established by means of a third baffle (11) having the hot gas inlet.
  • the assembly formed by the second baffle (3) and the manifold (9) are housed in the shell segment (7) having a larger section.
  • a coolant liquid inlet/outlet is located at the end of the shell corresponding to the fixed side and the other inlet/outlet is located at the opposite end.
  • the coolant inlet/outlet of the floating side is configured by means of a groove (7.1) arranged between the end of the shell segment (7) having a larger section and the third baffle (11).
  • This configuration has several technical effects, the first being that of placing this groove (7.1) in the area adjacent to the wall formed by the third baffle (11), preventing stagnation areas between the inlet/outlet and said third baffle (11), and the second being that of placing same in an area close to the elastically deformable conduit (10), favoring cooling thereof.
  • the elastically deformable conduit (10) is what receives the hot gas in a more direct manner when the heat exchanger is operating such that this part (10) is the part having a higher temperature.
  • the end position of the coolant inlet/outlet favors the entire length of this elastically deformable conduit (10) being suitably cooled, preventing device failure in this location.
  • the second baffle (3) and the manifold (9) also have a rectangular configuration. There is arranged between both components (3, 9) and the shell segment (7) having a larger section a space allowing passage of the coolant liquid since the inlet/outlet is located adjacent to the third baffle (3).
  • Streamlines extend primarily from the space between the tubes of the bundle of tubes (4) to the chamber (C), formed by the extension of the shell segment (7) having a larger section, surrounding the assembly formed by the second baffle (3) and the manifold (9).
  • These streamlines would contain one or more streamlines that would end in the second baffle, giving rise to a stagnation region were it not for the presence of a deflector (8) located between the assembly formed by the second baffle (3) and the manifold (9), and the shell segment (7) having a larger section.
  • This deflector (8) modifies the configuration of streamlines, preventing the symmetry that makes the streamlines tend to surround the entire second baffle (3).
  • the deflector (8) extends perimetrally around the assembly formed by the second baffle (3) and the manifold (9) in a segment equivalent to three of the four sides of the rectangular configuration of the second baffle (3) or with respect to the respective four sides of the rectangular configuration of the shell segment (7) having a larger section with which it establishes the closure.
  • the flow is therefore forced to only pass through one of the sides, making this preferred direction cause streamlines to run parallel to the second baffle (3), preventing stagnation regions.
  • closure on three of the four sides by means of a deflector (8) is established around the group formed by the second baffle (3)-manifold (9) assembly in a perimetral band spaced from the plane defined by the second baffle (3) in longitudinal direction X-X' towards the side opposite the fixed end of the heat exchanger.
  • Figure 5 shows a perspective view of the deflector (8) used in this embodiment in an essentially rectangular shape, configured for surrounding the second baffle (3) and the latter in turn surrounding the manifold (9).
  • the deflector (8) is manufactured from die-cut and bent plate. It internally has a perimetral band giving rise to the seat (8.1) which is supported on the surface of the second baffle (3).
  • the perimetral surface is formed by consecutively arranged sheets to prevent passage and to give rise to flexible elements that are arranged against the inner wall of the shell segment (7) having a larger section. These sheets are distributed perimetrally except on one side, in this case a smaller side, giving rise to a window (8.3) for passage of the coolant liquid.
  • Blocking of the flow by the deflector (8) like any other surface placed in the way of a flow, generates stagnation regions, precisely the effect to be prevented. Nevertheless, the configuration by means of sheets distributed with separations (8.2) prevents the formation of these stagnation or recirculation regions without preventing the sweeping effect of the stagnation regions from occurring in the second baffle (3).
  • Another technical solution adopted in this embodiment is the existence of a prolongation of the first tubular body of the shell (1) entering part of the chamber (C) formed by the shell segment (7) having a larger section.
  • the velocity of the velocity field in the chamber (C) and particularly the transverse flow running parallel to the second baffle (3) is increased.
  • the technical effect is better cooling of the second baffle (3), i.e., the baffle exposed to hot gas the most.
  • the increase in velocity is also observed inside the chamber (C) and therefore reduces new stagnation points generated by the deflector (8).
  • the embodiment of the invention also incorporates another way to additionally protect the elastically deformable conduit (10) from the high temperatures to which it is subjected given that the conduit directly receives the incoming hot gas.
  • the way to protect the inlet is by means of an intake deflector (12) configured by means of a tubular segment intended for being housed inside the elastically deformable conduit (10) but spaced from it.
  • the separation between the elastically deformable conduit (10) and the intake deflector (12) establishes a chamber insulating the elastically deformable conduit (10), reducing direct heat transfer from the hot gas flow. Not only does it establish a separation chamber but it also establishes guidance of the hot gas flow towards the central axis so that it does not hit the walls directly.
  • the tubular segment of the intake deflector (12) expands outwardly in order to be supported on the outer surface of the third baffle (11).
  • This configuration allows the third baffle (11), once it is attached to an outer flange, to leave this outer extension of the intake deflector (12) retained, achieving the fixing thereof.
  • This fixing does not require welding which, with abrupt temperature changes, would be damaged by the expansion stresses that would be produced.
  • this intake deflector (12) shows a perimetral rib (12.1) in the extension, which is achieved in this embodiment by means of deep-drawing, increasing the pressure with which the third baffle (11) and the outer flange are fixed.
  • the perimetral rib (12.1) is located on the outer face of the third baffle (11) for establishing a pressure type seat after establishing the attachment of the flange.
  • the section of Figures 1 and 2 shows the groove (7.1) of the coolant liquid inlet/outlet obtained by the spacing of the end edge of the shell segment (7) having a larger section with the third baffle (3).
  • a coolant liquid manifold (14) for receiving/supplying coolant liquid since said coolant liquid manifold (14) is in fluid communication with the groove (7.1) is formed in this embodiment by means of a die-cut outer plate.
  • the die-cut outer plate giving rise to the coolant liquid manifold (14) runs parallel to the outer edge of the third baffle (11), such that together with a flange (15) having greater resistance, the means of fixing with the outer flange which is not graphically depicted are defined.
  • the outer face of the third baffle (3) together with the perimetral rib (12.1) of the intake deflector (12) is the seat with which the heat exchanger is attached on the hot side to the outer flange connecting said heat exchanger with the hot gas uptake.
  • FIGS. 6 and 7 show another embodiment of the invention.
  • the shell segment (7) having a larger section has been obtained by deep-drawing the same plate of the main longitudinal segment of the shell (1) housing the bundle of tubes (4), thus generating a step between both segments (1, 7).
  • the shell (1) housing the bundle of tubes (4) comprises two pieces with a "U" section according to a cross section being joined together along two longitudinal welded lines.
  • the flow is forced to only pass through one of the sides of the deflector (8), making this preferred direction cause streamlines to run parallel to the second baffle (3), preventing stagnation regions.
  • the co-current flow shows a flow coming from the chamber (C) trying to flow according to the pressure gradient within the bundle of tubes (4); therefore, as soon as the flow enters into the space located within the bundle of tubes (4) it is oriented towards the fixed part of the heat exchanger preventing it to flow parallel to the second baffle (3) and then reducing the effect of the deflector (8).
  • a comb-shaped deflector (16) is located, according to the longitudinal direction X-X', in the chamber (C).
  • the comb-shaped deflector (16) comprises a transversal body (16.1) and a plurality of parallel projections (16.3) departing from said transversal body (16.1).
  • the parallel projections (16.3) are extended between two lateral plates (16.2).
  • the lateral plates (16.2) and the transversal body (16.1) shows one or more supports (16.5) configured by bending the plate in a perpendicular direction.
  • the comb-shaped deflector (16) is partially housed among the tubes of the bundle of tubes (4).
  • the transversal body (16.1) is housed between the bundle of tubes (4) and the shell segment (7) having a larger section, oriented transversal to the longitudinal direction X-X'.
  • the parallel projections (16.3) are inserted into the space between tubes of the bundle of tubes (4) and parallel to the second floating baffle (3), being said parallel projections (16.3) separated from the second floating baffle (3).
  • the comb-shaped deflector (16) comprises at least one support (16.5) in the transversal body (16.1), in the lateral plates (16.2) or in both.
  • the comb-shaped deflector (16) is fixed, for instance by brazing, or by fixing the supports (16.5) to the internal wall of the chamber (C), or by fixing the parallel projections (16.3) to the bundle of tubes (4).
  • the supports (16.5) are fixed to the internal wall of the chamber (C) while the parallel projections (16.3) are not; these parallel projections (16.3) are just abutting the tubes of the bundle of tubes (4) allowing said bundle of tubes (4) to expand when heated by the hot gas.
  • the comb-shaped deflector (16) shows a further seat surface (16.3.1) in the parallel projections (16.3), in this embodiment by bending the plate, allowing the comb-shaped deflector (16) to rest on the surface of the bundle of tubes (4), at least in a portion of said seat surface (16.3.1).
  • the seat surface (16.3.1) has at least a first straight portion (a) abutting one flat face of a heat exchanger tube, a second arched portion (b) abutting the curved side of the heat exchanger tube; and, a third straight portion (c) parallel to the opposite flat face of the heat exchanger tube.
  • this step (s) defining the separation between the parallel projection (16.3) and the flat face of the heat exchanger tube.
  • the separation between the opposite flat side of the heat exchanger tube and the third straight portion (c) allows the flow sweeping any stagnation region of the flow located adjacent to the parallel projections (16.3) of the comb-shaped deflector (16).
  • the step (s) is a curved step.
  • the seat surface (16.3.1) is obtained by using a thicker plate provided with an edge wide enough for allowing a seat surface (16.3.1) with a resting surface rather than using a bended portion of the plate.
  • the third straight portion (c) is also abutting the opposite flat face of the heat exchanger tube allowing to deflect the whole flow of the surrounding region.
  • the comb-shaped deflector (16) further comprises a plurality of windows (16.4) adjacent to the seat surfaces (16.3.1) allowing the flow to pass through, preventing stagnation regions generated by the main surface of the transversal body (16.1).
  • the plurality of windows (16.4) are located out of the bundle of tubes (4), next to the space between heat exchanger tubes; that is, each window (16.4) is located in correspondence with each space between two flat heat exchanger tubes.
  • the inlet has a connecting piece (17) as an interface between a connecting tube (not shown) and the third baffle (11).
  • This connecting piece (17) has two different sections in the hole allowing the flow to pass through, a small section in the outer part of the hole and a large section in the inner part of the hole, both different sections separated by a step (17.1).
  • the shape of the connecting piece (17) located at the inlet causes a hot gas jet with a diameter smaller that the large section; therefore, the hot gas at the inlet does not impinge directly over the inner wall of the internal conduit protecting it against high temperatures.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Fluid Mechanics (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (16)

  1. Wärmetauschvorrichtung zur Kühlung eines heißen Gases mittels einer Kühlflüssigkeit, umfassend:
    ein Bündel von Wärmetauschrohren (4), die sich in einer Längsrichtung (X-X') zwischen einem feststehenden ersten Prallblech (2) und einem schwebenden zweiten Prallblech (3) erstrecken und in denen das zu kühlende heiße Gas strömt, einen das Rohrbündel (4) aufnehmenden Mantel (1), wobei die Kühlflüssigkeit in dem Zwischenraum zwischen dem Mantel (1) und dem Rohrbündel (4) strömen kann, wobei:
    - der Mantel (1) an einem Ende durch das feststehende erste Prallblech (2) verschlossen ist und an dem gegenüberliegenden Ende eine Kammer (C) umfasst, die durch eine Verlängerung in Form eines Mantelsegments (7) gebildet ist, das einen größeren Querschnitt aufweist und von einem dritten Prallblech (11) verschlossen ist, und
    - sich ein erster Kühlflüssigkeitseinlass/-auslass an einer Stelle des Mantels (1) auf der Seite des ersten Prallblechs (2) befindet und ein zweiter Kühlflüssigkeitseinlass/-auslass an einer Stelle des einen größeren Querschnitt aufweisenden Mantelsegments (7) eingerichtet ist,
    wobei das schwebende zweite Prallblech (3) ein Anschlussstück (9) aufweist, das mit dem Einlass der Wärmetauschrohre (4) in Fluidverbindung steht, und das Anschlussstück (9) wiederum mit einem in dem dritten Prallblech (11) angeordneten Einlass für das heiße Gas in Fluidverbindung steht, wobei diese Fluidverbindung über eine elastisch verformbare Leitung (10) zumindest entlang der Längsrichtung (X-X') erfolgt,
    das schwebende zweite Prallblech (3) zusammen mit dem Anschlussstück (9) eine Anordnung bildet, die in der durch das einen größeren Querschnitt aufweisende Mantelsegment (7) gebildeten Verlängerung aufgenommen ist und an dem Umfang der Anordnung (3, 9) um einen Abstand von dem Mantelsegment (7) beabstandet ist, so dass die Kühlflüssigkeit strömen kann; und die Stelle des einen größeren Querschnitt aufweisenden Mantelsegments (7), an welcher sich der zweite Kühlflüssigkeitseinlass/-auslass befindet, in der Längsrichtung (X-X') zwischen der Anordnung aus dem schwebenden zweiten Prallblech (3) und dem Anschlussstück (9) und dem dritten Prallblech (11) liegt,
    dadurch gekennzeichnet, dass
    in dem Umfangsabstand zwischen der Anordnung aus dem schwebenden zweiten Prallblech (3) und dem Anschlussstück (9) und dem einen größeren Querschnitt aufweisenden Mantelsegment (7) eine Umlenkeinrichtung (8) angeordnet ist, die den Abstand zwischen der Anordnung (3, 9) und dem einen größeren Querschnitt aufweisenden Mantelsegment (7) zumindest entlang eines Abschnitts des Umfangsabstands bedeckt.
  2. Vorrichtung nach Anspruch 1, wobei die aus dem schwebenden zweiten Prallblech (3) und dem Anschlussstück (9) gebildete Anordnung am Umfang im Wesentlichen rechteckig ausgebildet ist und wobei die Umlenkeinrichtung (8) mindestens drei Seiten der Anordnung bedeckt.
  3. Vorrichtung nach einem der vorhergehenden Ansprüche, wobei die elastisch verformbare Leitung (10) in der Art eines Faltenbalgs ausgebildet ist.
  4. Vorrichtung nach einem der vorhergehenden Ansprüche, wobei der Heißgaseinlass eine Einlassumlenkeinrichtung (12) aufweist, die durch ein röhrenförmiges Segment gebildet ist, das sich in die elastisch verformbare Leitung (10) verlängert, um den eintretenden heißen Gasstrom auf ihre Längsmittelachse zu lenken, so dass die elastisch verformbare Leitung (10) vor Hitze geschützt ist.
  5. Vorrichtung nach Anspruch 4, wobei das dritte Prallblech (11) als Befestigungsflansch der Wärmetauschvorrichtung ausgebildet ist und wobei die Einlassumlenkeinrichtung (12) an der Außenseite des dritten Prallblechs (11) eine Umfangsrippe (12.1) aufweist, die nach der Befestigung des Flansches eine Presspassung herstellt.
  6. Vorrichtung nach einem der Ansprüche 1 bis 3, wobei der Heißgaseinlass an dem Einlass für das heiße Gas ein Verbindungsstück (17) aufweist, das einen äußeren kleinen Querschnitt und einen inneren großen Querschnitt aufweist, um die Innenwand der inneren Leitung vor hohen Temperaturen zu schützen.
  7. Vorrichtung nach einem der vorhergehenden Ansprüche, wobei der zweite Kühlflüssigkeitseinlass/-auslass entlang einer Nut (7.1) ausgebildet ist, die sich zwischen einem Abschnitt des freien Rands des einen größeren Querschnitt aufweisenden Mantelsegments (7) und dem dritten Prallblech (11) befindet.
  8. Vorrichtung nach Anspruch 7, wobei das Kühlflüssigkeitsanschlussstück (14) auf der schwebenden Seite durch eine Platte, die sich von dem einen größeren Querschnitt aufweisenden Mantelsegment (7) zu dem die Nut (7.1) innen aufnehmenden dritten Prallblech (11) nach außen erstreckt, und Anordnen des Kühlflüssigkeitseinlasses/-auslasses in der Platte ausgebildet ist.
  9. Vorrichtung nach einem der vorhergehenden Ansprüche, wobei das Rohrbündel (4) ein oder mehrere Stützprallbleche (5) aufweist, die
    - entweder mit dem Mantel (1) verbunden sind, ohne die Längsbewegung des sie durchquerenden Rohrbündels (4) einzuschränken; oder
    - mit dem sie durchquerenden Rohrbündel (4) verbunden sind, ohne die Längsbewegung gegenüber dem Mantel (1) einzuschränken.
  10. Vorrichtung nach einem der vorhergehenden Ansprüche, wobei der das Rohrbündel (4) aufnehmende Mantel (1) an einem Teil seines Umfangs oder an seinem gesamten Umfang in der Längsrichtung (X-X') verlängert ist, so dass er zur Erhöhung der Kühlflüssigkeitsgeschwindigkeit in der Kammer (C) teilweise in die Kammer (C) eintritt, die durch die Verlängerung in Form des einen größeren Querschnitt aufweisenden Mantelsegments (7) gebildet ist.
  11. Vorrichtung nach einem der vorhergehenden Ansprüche, des Weiteren umfassend eine kammförmige Umlenkeinrichtung (16) in der Kammer (C), wobei die kammförmige Umlenkeinrichtung (16) einen sich quer erstreckenden Körper (16.1) und eine Vielzahl von sich parallel zueinander erstreckenden Vorsprüngen (16.3) aufweist, die von dem sich quer erstreckenden Körper (16.1) ausgehen; wobei:
    - der sich quer erstreckende Körper (16.1) zwischen dem Rohrbündel (4) und dem einen größeren Durchmesser aufweisenden Mantelsegment (7) aufgenommen und quer zu der Längsrichtung (X-X') ausgerichtet ist; und
    - die Vielzahl von sich parallel zueinander erstreckenden Vorsprüngen (16.3) in den Zwischenraum zwischen Rohren des Rohrbündels (4) eingesetzt sind und parallel zu dem zweiten Prallblech (3) angeordnet sind.
  12. Vorrichtung nach Anspruch 11, wobei die kammförmige Umlenkeinrichtung (16) des Weiteren zwei seitliche Platten (16.2) umfasst, die derart angeordnet sind, dass sich die Vielzahl von sich parallel zueinander erstreckenden Vorsprüngen (16.3), die von dem sich quer erstreckenden Körper (16.1) ausgehen, zwischen den seitlichen Platten (16.2) befinden; und wobei sich die seitlichen Platten (16.2) zu beiden Seiten des Rohrbündels (4) zwischen dem Rohrbündel (4) und dem einen größeren Querschnitt aufweisenden Mantelsegment (7) erstrecken.
  13. Vorrichtung nach einem der Ansprüche 10 oder 11, wobei die kammförmige Umlenkeinrichtung (16) in dem sich quer erstreckenden Körper (16.1) in mindestens einer seitlichen Platte (16.2) oder in beiden seitlichen Platten (16.2) mindestens eine Halterung (16.5) umfasst.
  14. Vorrichtung nach Anspruch 13, wobei die kammförmige Umlenkeinrichtung (16) entweder durch Befestigen der Halterungen (16.5) an der Innenwand der Kammer (C) oder alternativ durch Befestigen der sich parallel zueinander erstreckenden Vorsprünge (16.3) an dem Rohrbündel (4) befestigt ist.
  15. Vorrichtung nach einem der Ansprüche 10 bis 13, wobei die sich parallel zueinander erstreckenden Vorsprünge (16.3) eine Sitzfläche (16.3.1) aufweisen, die zur Anlage an der Oberfläche der Wärmetauscherrohre ausgebildet ist; und wobei mindestens einer der sich parallel zueinander erstreckenden Vorsprünge (16.3) zur Vermeidung von Staubereichen einen Sitzflächenabschnitt (16.3.1) mit einer Vertiefung aufweist, der von der Oberfläche des Wärmetauschers beabstandet ist, so dass der Strom hindurchströmen kann.
  16. AGR-System für Fahrzeuge mit Verbrennungsmotor, umfassend einen Wärmetauscher nach einem der vorhergehenden Ansprüche.
EP16165749.9A 2015-04-20 2016-04-18 Wärmetauschervorrichtung Active EP3086075B1 (de)

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KR20160124701A (ko) 2016-10-28
CN106066128B (zh) 2020-05-12
CN106066128A (zh) 2016-11-02
US10495385B2 (en) 2019-12-03
BR102016008959A2 (pt) 2016-11-01
US20160305713A1 (en) 2016-10-20
EP3086075A1 (de) 2016-10-26

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